JP2565596Y2 - Transmission for diesel vehicles - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission for a diesel vehicle, and more particularly, to selectively switching the output of an engine .
Transmitted to the transmission through the Luc converter ,
The present invention relates to a transmission for a diesel vehicle that transmits power to an output shaft by shifting the transmission in three stages.

[0002]

2. Description of the Related Art Generally, in diesel vehicles,
A transmission consisting of a fluid transmission and a transmission is installed between the output shaft of the engine and the axle of the vehicle. At the time of starting, the output torque of the engine is transmitted to the transmission via the torque converter, and is required at the time of starting. When a large torque is secured and thereafter the speed is increased, the required output torque decreases. Therefore, the output from the engine is directly transmitted to the transmission without passing through a torque converter.

[0003] Such a transmission for a diesel vehicle needs to use the output of the engine effectively from a low speed range to a high speed range, so that it operates through a torque converter (hereinafter referred to as "shift operation"). In many cases, a transmission having one speed stage and two speed stages for an operation that does not go through the speed stage (hereinafter, referred to as “direct operation”) is used.

Further, in order to further increase the speed of a vehicle with a diesel engine having substantially the same performance as that of a conventional engine (hereinafter simply referred to as "engine"), the speed gear is increased by one gear and the gear ratio of the final gear is made larger than the current gear ratio. From the viewpoint of the transmission, that is, the high speed rotation of the wheels and the maintenance of the traction force, one stage of the speed change operation, the direct connection operation 3
A gear transmission is desired. In this case, the transmission is required to be concentric with the transmission input shaft and the output shaft in relation to the engine arrangement.

Here, a conventional design example of a direct-coupled three-stage transmission in which a transmission input shaft and an output shaft are concentrically arranged will be described with reference to FIG. 2, power from an engine (not shown) is transmitted from an input shaft 1 of a transmission to a transmission input shaft 4 via a direct coupling clutch 2 and a torque converter 3. The transmission input shaft 4 and the output shaft 20 are arranged concentrically depending on the arrangement of the engine.

In order to obtain a forward and reverse three-speed shift, first,
A first-speed forward shaft 52 having a first-speed forward shaft gear 32 that meshes with the input shaft pinion 31 of the transmission input shaft 4 includes:
A clutch drum 56 formed integrally with a clutch portion 52b constituting the forward first speed clutch 51 and a clutch portion 52a constituting the reverse first speed clutch 50 is provided integrally.
In the forward first speed clutch 51, the clutch portion 52b and the forward first speed gear 41 meshing with the output shaft large gear 42 of the output shaft 20 are provided.
And the reverse first speed clutch 50
The clutch portion of the reverse first speed gear 38 meshing with the clutch portion 52a and the first speed reverse shaft gear 39 of the first speed reverse shaft 53 having at one end a first speed reverse shaft gear 40 meshing with the output shaft large gear 42 of the output shaft 20. 38a are fitted. In addition, advance 1
The speed gear 41 and the reverse first speed gear 38 are rotatably supported by a first speed forward shaft 52.

Next, a forward shaft 54 having a forward shaft small gear 33 meshing with the input shaft large gear 30 of the transmission input shaft 4 has a forward shaft 2 with a forward shaft large gear 34 meshing with a reverse shaft gear 35 of a reverse shaft 55. A clutch drum 58 is formed integrally with a clutch portion 54b constituting the high speed clutch 47 and a clutch portion 54a constituting the third forward speed clutch 46. The clutch portion 54b and the output of the forward second speed clutch 47 are provided integrally. An output shaft large gear 42 of the shaft 20 is engaged with a clutch portion 44a of a forward second speed gear 44 that meshes with the clutch portion 54a of the forward third speed clutch 46.
The clutch portion 36a of the third forward gear 36 meshing with the output shaft small gear 43 is fitted. The second forward gear 44 and the third forward gear 36 are rotatably supported by a forward shaft 54.

Further, a reverse shaft 55 having a reverse shaft gear 35 meshing with the forward shaft large gear 34 of the forward shaft 54 has a clutch portion 55b constituting a reverse second speed clutch 49 and a reverse
A clutch drum 57 formed adjacent to a clutch portion 55a constituting the high speed clutch 48 is provided integrally. In the reverse second speed clutch 49, the clutch portion 55b and the output shaft 2 are provided.
0 is engaged with the clutch portion 45a of the reverse second speed gear 45 which meshes with the output shaft large gear 42, and the clutch portion 55a and the output shaft small gear 4 of the output shaft 20 are engaged with the reverse third speed clutch 48.
3 engages with the clutch 37a of the gear 37. The reverse second speed gear 45 and the reverse third speed gear 37 are rotatably supported by a reverse shaft 55.

The power transmission path at each speed stage is as follows. First forward speed: transmission input shaft 4 → input shaft small gear 31 → first speed forward shaft gear 32 → first speed forward shaft 52 → forward first speed clutch 51 (fitting) → forward first speed gear 41 → output shaft large gear 42 → Output shaft 20 2nd forward speed: Transmission input shaft 4 → input shaft large gear 30 → forward shaft small gear 33 → forward shaft 54 → forward 2nd speed clutch 47 (fitting) → forward 2nd speed gear 44 → output shaft large gear 42
→ Output shaft 20 Third forward speed: Transmission input shaft 4 → Input shaft large gear 30 → Forward shaft small gear 33 → Forward shaft 54 → Forward third speed clutch 46 (fitting) → Forward third speed gear 36 → Output shaft small gear 43
→ output shaft 20 reverse first speed: transmission input shaft 4 → input shaft small gear 31 → first speed forward shaft gear 32 → first speed forward shaft 52 → reverse first speed clutch 50 (fitting) → reverse first speed gear 38 → first speed Reverse shaft gear 39 → first speed reverse shaft 53 → first speed reverse shaft gear 40 → output shaft large gear 42 → output shaft 20 second reverse speed: transmission input shaft 4 → input shaft large gear 30 → forward shaft small gear 33 → forward shaft 54 → Advance shaft gear 3
4 → reverse shaft gear 35 → reverse shaft 55 → reverse second speed clutch 4
9 (mating) → reverse second speed gear 45 → output shaft large gear 42 → output shaft 20 reverse third speed: transmission input shaft 4 → input shaft large gear 30 → forward shaft small gear 33 → forward shaft 54 → forward shaft large gear 3
4 → reverse shaft gear 35 → reverse shaft 55 → reverse 3rd speed clutch 4
8 (mating) → reverse third speed gear 37 → output shaft small gear 43 → output shaft 20

[0010]

The conventional three-speed transmission has, for example, six shafts including an input shaft, sixteen gears, and six clutches as shown in the example of FIG. As the number of sets, shafts, gears and clutches used increases, the size and weight of the transmission for a high-speed vehicle which is directly affected by the weight of the device are too large. What
In addition, construction of industrial vehicles such as forklifts and tire rollers
The transmission of the construction machine has 5 shafts, 12 gears, and
It is also known to use five clutches to reduce the size of the apparatus (see Japanese Patent Application Laid-Open No. 3-219152), but the dimensions and weight are still insufficient.

SUMMARY OF THE INVENTION An object of the present invention is to solve such a problem. In a transmission of a direct connection type three-stage transmission in which an input shaft and an output shaft are concentrically arranged, a shaft, a gear, and a clutch are provided. The present invention is to provide a transmission suitable for use in a lightweight and compact diesel vehicle by minimizing the number of the transmissions.

[0012]

In order to achieve the above-mentioned object, the present invention selectively transmits the output of an engine to a transmission via a torque converter, and shifts the output of the engine to three stages to output shaft. A transmission for transmitting power to a diesel vehicle, wherein the transmission is provided with an input shaft 4 having an input shaft gear 5, arranged concentrically with the input shaft 4, and having an output shaft gear 11 and a third speed clutch 1.
Output shaft 20 having a clutch portion 20a constituting
And a first-speed shaft 2 that is disposed in parallel with the input shaft 4 and has the clutch portions 21 a and 21 b and the first-speed shaft gear 12 that constitute the adjacent reverse clutch 15 and first-speed clutch 16.
1 and each of the clutch portions 22a and 22b constituting the adjacent forward clutch 17 and the second speed clutch 18 similarly arranged in parallel with the input shaft 4, and the second speed shaft gear 13 meshing with the first speed shaft gear 12. A second-speed shaft 22, and a clutch portion 14a constituting the third-speed clutch 19;
The second speed shaft gear 13 rotatably supported by the output shaft 20
A third speed gear 14 meshing with the input shaft gear 5 having a clutch portion 6a constituting the forward clutch 17 and rotatably supported by a second speed shaft 22 and meshing with the input shaft gear 5;
It has a clutch portion 7a constituting the reverse clutch 15, has a reverse gear 7 rotatably supported on the first speed shaft 21 and meshes with the input shaft gear 5, and has a clutch portion 8a constituting the first speed clutch 16. A first speed gear 8 rotatably supported by the first speed shaft 21 and meshing with the intermediate gear 9; and a clutch portion 10a constituting the second speed clutch 18. The first speed gear 8 is rotatably supported by the second speed shaft 22 for output. In a transmission for a diesel vehicle comprising a shaft gear 11 and a second speed gear 10 meshing with each other, the intermediate gear 9 is formed integrally with the second speed gear 10,
It is rotatably supported on the second speed shaft 22.

[0013]

According to the structure of the present invention, the intermediate gear meshing with the first speed gear is integrally formed with the second speed gear and is rotatably supported on the second speed shaft. It can be performed with four shafts including the shaft, ten gears and five clutches.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to a diesel vehicle transmission shown in the drawings.

The transmission comprises a fluid transmission (not shown) and a transmission (not shown), and the engine is connected to the input shaft 1 on the input side of the fluid transmission via a flywheel (not shown) and an elastic joint. . The input shaft 1 has a direct coupling clutch 2 composed of a hydraulic friction clutch.
The output from the engine is transmitted to the transmission input shaft 4 via the torque converter 3 or not, by engaging and disengaging the direct coupling clutch 2. I do.

The transmission input shaft 4 and its output shaft 20 are arranged concentrically. The transmission input shaft 4 is provided with an input shaft gear 5, and the output shaft 20 is provided with:
The output shaft gear 11 and a clutch portion 20 a constituting the third speed clutch 19 are provided. Therefore, the input shaft gear 5
Is transmitted to the output shaft gear 11 or the third speed clutch 19 via each gear and each clutch described below, and is transmitted to the output shaft 20.

A first speed shaft 21 and a second speed shaft 22 are arranged in parallel with the transmission input shaft 4 and at equal distances between the shafts, and the first speed shaft 21 has clutch portions 21a and 1 A clutch drum 21 provided with a clutch portion 21b adjacent to the speed clutch 16 and provided with the first-speed shaft gear 12 is provided. A clutch portion 22a included in the forward clutch 17 A clutch drum 24 provided with a clutch portion 22b constituting the clutch 18 adjacent thereto and provided with the second speed shaft gear 13 is provided. The first speed gear 12 and the second speed gear 13 are in meshing relationship.

The clutch portion 22 of the output shaft 20
a which constitutes the third speed clutch 19 together with the clutch portion 14a
Is rotatably supported by the output shaft 20 and meshes with the second speed gear 13. The third speed gear 14 and the first speed shaft gear 12 provided on the first speed shaft 21 are displaced in the axial direction so as not to directly mesh with each other and mesh with the second speed shaft gear 13 respectively.

Further, the clutch portion 22 of the second speed shaft 22
The forward gear 6 having a clutch portion 6a that constitutes the forward clutch 17 together with the input shaft gear 5 is rotatably supported by the second speed shaft 22. Similarly, the reverse gear 7 having the clutch portion 7a constituting the reverse clutch 15 together with the clutch portion 21a of the first speed shaft 21
1 and rotatably supported by the input shaft gear 5.

The clutch portion 21b of the first speed shaft 21
A first-speed gear 8 having a clutch portion 8a constituting a first-speed clutch 16 is rotatably supported on the first-speed shaft 21 on the side opposite to the reverse gear 7, and is an intermediate gear integrated with a second-speed gear 10 described later. 9 is engaged. A second speed gear 10 having a clutch portion 10a that constitutes the second speed clutch 18 together with the clutch portion 22b of the second speed shaft 22 is rotatably supported on the second speed shaft 22 at a side opposite to the forward gear 6 and an output shaft. And 20 output shaft gears 11. Note that this 2
The speed gear 10 has fewer teeth than the integral intermediate gear 9,
It should be understood that first gear 8 is transmitting power to output shaft 20 at reduced speed.

The power transmission path of the transmission from the first speed to the third speed is as follows. First forward speed: Transmission input shaft 4 → input shaft gear 5
→ forward gear 6 → forward clutch 17 → second speed shaft gear 13 → 1
Speed shaft gear 12 → first speed clutch 16 → first speed gear 8 → intermediate gear 9 → second speed gear 10 → output shaft gear 11 → output shaft 20 forward second speed: transmission input shaft 4 → input shaft gear 5
→ forward gear 6 → forward clutch 17 → second speed clutch 18 →
2nd speed gear 10 → output shaft gear 11 → output shaft 20 3rd forward speed: transmission input shaft 4 → input shaft gear 5
→ forward gear 6 → forward clutch 17 → second speed shaft gear 13 → 3
Speed gear 14 → third speed clutch 19 → output shaft 20 reverse first speed: transmission input shaft 4 → input shaft gear 5
→ reverse gear 7 → reverse clutch 15 → 1st speed clutch 16 →
1st gear 8 → intermediate gear 9 → 2nd gear 10 → output shaft gear 1
1 → output shaft 20 reverse 2nd speed: transmission input shaft 4 → input shaft gear 5
→ reverse gear 7 → reverse clutch 15 → 1st speed gear 12 → 2
Speed shaft gear 13 → second speed clutch 18 → second speed gear 10 → output shaft gear 11 → output shaft 20 Third reverse speed: transmission input shaft 4 → input shaft gear 5
→ reverse gear 7 → reverse clutch 15 → 1st speed gear 12 → 2
Speed shaft gear 13 → third speed gear 14 → third speed clutch 19 → output shaft 20

[0022]

According to the present invention, an intermediate gear meshing with a first-speed gear is provided in a transmission for a diesel vehicle in which a transmission input shaft and an output shaft are concentrically arranged and a forward-reverse and reverse-drive three-speed transmission can be switched. Because it is integrated with the second speed gear and rotatably supported on the second speed shaft, the front and rear three-speed shifting can be performed with four shafts including the input shaft, ten gears and five clutches. Therefore, the transmission for a diesel vehicle can be made lightweight and compact, which can contribute to speeding up of the vehicle.

[Brief description of the drawings]

FIG. 1 is a schematic view of a diesel vehicle transmission showing an embodiment of the present invention.

FIG. 2 is a schematic view of a conventional three-speed transmission.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Direct-coupled clutch 3 Torque converter 4 Transmission input shaft 5 Input shaft gear 6 Forward gear 6a Clutch part 7 Reverse gear 7a, 8a, 10a Clutch part 8 1st gear 9 Intermediate gear 10 2nd gear 11 Output shaft gear 12 1 Speed shaft gear 13 second speed shaft gear 14 third speed gear 15 reverse clutch 16 first speed clutch 17 forward clutch 18 second speed clutch 19 third speed clutch 20 output shaft 20a, 21a, 22a clutch part 21 first speed shaft 22 second speed shaft 23, 24, 25 Drum clutch 30 Input shaft large gear 31 Input shaft small gear 32 First speed forward shaft gear 33 Forward shaft small gear 34 Forward shaft large gear 35 Reverse shaft gear 36 Forward third speed gear 36a, 37a, 38a Clutch portion 37 Reverse 3 Speed gear 38 reverse first speed gear 39,40 first speed reverse shaft gear 41 forward first speed gear 4 1a, 44a, 45a Clutch part 42 Output shaft large gear 43 Output shaft small gear 44 Forward second speed gear 45 Reverse second speed gear 46 Forward third speed clutch 47 Forward second speed clutch 48 Reverse third speed clutch 49 Reverse second speed clutch 50 Reverse 1 Speed clutch 51 forward first speed clutch 52 first speed forward shaft 53 first speed reverse shaft 54 forward shaft 55 reverse shaft 52a, 52b, 54a, 54b, 55a, 55b
Clutch section

Claims (1)

(57) [Scope of request for utility model registration] 1. A transmission for a diesel vehicle that selectively transmits the output of an engine to a transmission via a torque converter, and shifts the transmission into three stages to transmit power to an output shaft. A transmission input shaft 4 having an input shaft gear 5, an output shaft 20 which is arranged concentrically with the transmission input shaft 4 and has an output shaft gear 11 and a clutch portion 20 a constituting a third speed clutch 19, A first-speed shaft 2 that is arranged in parallel with the input shaft 4 and has respective clutch portions 21a and 21b and a first-speed shaft gear 12 that constitute the adjacent reverse clutch 15 and first-speed clutch 16;
1 and each of the clutch portions 22a and 22b constituting the adjacent forward clutch 17 and the second speed clutch 18 similarly arranged in parallel with the input shaft 4, and the second speed shaft gear 13 meshing with the first speed shaft gear 12. A second-speed shaft 22, and a clutch portion 14a constituting the third-speed clutch 19;
The second speed shaft gear 13 rotatably supported by the output shaft 20
A third speed gear 14 meshing with the input shaft gear 5 having a clutch portion 6a constituting the forward clutch 17 and rotatably supported by a second speed shaft 22 and meshing with the input shaft gear 5;
A reverse gear 7 rotatably supported by the first speed shaft 21 and meshing with the input shaft gear 5; and a clutch portion 8a configuring the first speed clutch. A first speed gear 8 rotatably supported on the first speed shaft 21 and meshing with the intermediate gear 9; and a clutch portion 10a constituting the second speed clutch 18;
In a transmission for a diesel vehicle, which comprises a second speed gear 10 rotatably supported by and meshing with an output shaft gear 11,
A transmission for a diesel vehicle, wherein the intermediate gear 9 is formed integrally with a second speed gear 10 and is rotatably supported on a second speed shaft 22.